Hydraulic feed and control mechanism



Oct. 10, 1950 w. F. GROENE ETAL. 2,525,127

I HYDRAULIC FEED AND CONTROL MECHANISM Original Filed Jan. 11, 1945 I 5 Sheets-Sheet 1 D E iflhl T, T T T e VARIABLE FINE FEED H '03 RAPID coARsE FEED TRAV. -DWELL COARSE FEED \LDWELL RAPID VARIABLE FlNE FEED TRAv.

D E I F3; Ia

MAxIMuM RAPID TRAV. D I I J SPINDLE SPEED v SPINDLE UP AT DWELL SPEED RATE coARsE FEED VARIABLE G FINE FEED H I DISTANCE 0F 0 TOOL TRAVEL DWELL I FIG. ]I

INVENTORS.

WILL/AM F. GROE/VE, HAROLD J. S/EKMA/VN B AND WALTER R. MEYER i-TM A TTORA/EYS.

Oct. 10, 1950 w. F. GROENE ETAL 2,525,127

I HYDRAULIC FEED AND CONTROL MECHANISM Original Filed Jan. 11, 1945 5 Sheets-Sh ee t 2 IIOQ v INVENTORS. W/LL/AM F. GROE/VE, HAROLD J. S/E/(MA/VN BY AND WALTER R. MEYER ATTORNEYS.

Oct. 10, 1950 w, GRQENE ET AL 2,525,127

HYDRAULIC FEED AND CONTROL MEQHANISM Original Filed Jan. 11, 1945 5 S he etsSheet 5 IN VEN TORS. W/LL/AM F. GROENE,

HAROLD J. S/EKMAN/V I I E Y BY MD WALTER R. MEYER Oct. 10, 1950 w. F. GROENE ETAL HYDRAULIC FEED AND CONTROL MECHANISM- Original File d Jan. '11; '1945 5 Sheets-Sheet 4 INVENTORS. w IAM F. mom/5, HA D J. SlE/(MA/VIV BY AND WALTER RMEYER A TTOff/VEYS.

w. F. GROENE ETAL 2,525,127 HYDRAULIC FEED AND CONTROL MECHANISM Original FiledJan. 11, 1945 '5 Sheets-She s ..NR amww m M ME E n m NG/R. 0 E 3 J3 T MDTS A umm MM M mm Y B Patented Oct. 10, 1950 2,525,121 masonic ram AND cosraon MECHANISM William F. Greene, Harold J. Siekmann, and

Walter E. Meyer, Cincinnati, Ohio, assignors to v The B. K. Le Blond Machine Tool Company, Cincinnati, Ohio, a corporation of Delaware Original application January 11, 1945, Serial No.

" 572,388, now Patent No. 2,470,304, dated May 17, 1949. Divided and this application March .26, 1946, Serial No. 657,272

This invention relates to hydraulic and electric control mechanism for lathes, particularly lathes of the center drive type intended for machining the bearing portions of crankshafts or similar work pieces. The machine we have selected for illustrating our invention is intended more particularly for simultaneous machining of the stub end, flange end, cheek portions of the webs, and the line bearings of multi-throw crankshafts such as are used in multi-cylinder internal combustion engines.

The application is a divisional application of original application, Serial No. 572,388, filed January 11,1945, now Patent No. 2,470,304, issued May 17, 1949.

One of the objects of this invention is to provide a hydraulic and electrical control system for automatically determining a sequential selection of feed movements for the tools and rate of rotation of the work piece during an automatic machining cycle.

A further object of this invention is to provide an improved electric hydraulic control mechanism for a crankshaft lathe for automatically regulating the .rate of feed and spindle speed in a most efllcient manner to produce a work piece of a high degree of accuracy and-a fine finish.

A further object is to provide a hydraulic and electric control system for a machine in which the tools are automatically controlled in rapid traverse movement toward the work, automatically slowed just before the cutting begins, and controlled in slow feeding movement into the work at a speed which may be varied as desired, while automatically speeding up rotation of the work piece as the cutting tools reach the final desired depth of cut on the completed work.

And still another object of this invention is to provide a fully automatic crankshaft lathe feed control and operating mechanism through the use of an inter-related hydraulic and. electrical system including control valves and switch mechanism operated in a predetermined sequential relationship by the retracting and advancing movement of the tool relative to the work. 4

Still another object is to provide a hydraulic operating system for a lathe which is controlled by a disc carrying a plurality of cams adjustable about the periphery thereof, each cam controlling an appropriate electric controlswitch or hydraulic valve for regulating said hydraulic system, the cam disc being rotated in control movement by the relative movement of work and tool of the machine.

Further features and advantages of this invention will appear from a detailed description of the'drawings in which:

6 Claims. (Cl. 60 -52) Figure I is a diagrammatic view showing the typical relationship of work and tool in a crankshaft turning operation in a machine to which this novel hydraulic and electric system is preferably adapted.

Figure Ia is a view comparable but taken on a plane normal thereto.

Figure II shows the relative rate of movement of work and tool during a complete machining cycle in a machine incorporating the features of this invention.

Figure III is a diagrammatic view of the hydraulic circuit shown applied to a typical crankshaft lathe tool bar feed mechanism including the segmental cam control disc and associated control mechanisms, incorporating the features of this invention.

Figure IV is an enlarged view of the segmental cam control disc shown in the position of full retraction of the cutting tools at the beginning of a cutting cycle.

Figure V is a similar enlarged view to that of Figure IV but showing the segmental cam control disc in the position of full infeed movement of the tools to depth into the work.

Figure VI is an enlarged sectional view of the control mechanism for actuating the feed rate control valve indicated on the line VI-VI of Figure VII.

Figure- VII is an enlarged sectional view of the same control-mechanism shown in Figure VI but indicated on the line VII-VII in Figure VI.

Figure VIII is a sectional view on the line VIII-VIII of Figure VI showing in articular the eccentric mounting provided for fine adjustment of the feed rate control valve actuating roller.

Figure IX is an elementary wiring diagram showing the circuit for the hydraulic valve conto Figure I trolling solenoids, the main drive motor, and the hydraulic system drive motor.

A typical crankshaft turning operation to be carried out and controlled by applicants hydraulic and electric control mechanism is illustrated in Figures I and la, where is shown the relationship of work and tool during a complete machining cycle.

The work crankshaft W comprises a web or cheek portion A having anintegral pin or line bearing portion B. The stock to be removed from these portions of the crankshaft is indicated by the broken section lines C. Cutting tools, only one of which is here shown; are usually fed from diametrically opposite directions relative to the axis I03 of the pin or hearing portion on the work axis of the lathe. The tool starts from the initial retracted position D and is actuated at a rapid traverserate until it arrives at position E of initial engagement with the material C to be cut away from the cheek face F of the crankshaft web A. The tool-is then reduced in rate of feed movement to a coarse feed while it cuts down the cheek face F and comes into initial cutting contact with the metalC surrounding the pin or bearing portion B of the crankshaft as indicated at G. At this point, the feed movement of the tool is still further reduced to a fine decreasing feeding movement as it continues to depth or dwell position at H where the tool is brought to a definite predetermined fixed stop position relative to the work axis I03 around which the work piece is rotating. The tool is then held in this depth or dwell position for several revolutions of the work piece in finish a highly accurate polished surface on the bearing B. After the completion of this finishing operation, the tool is then rapidly retracted back to initial starting position D.

The rate of rotation of the work is also automatically' controlled in a predetermined sequential relationship with the above mentioned feed rate variation of the cutting tools. This is clearly illustrated in the diagram, Figure II, wherein it will be seen that during the initial infeed movement of the tool through rapid traverse, coarse feed, and fine feed to dwell position the rotation of the work piece is maintained at a predetermined relatively slow spindle speed indicated at I in the diagram. As the cutting tools approach the dwell position H, the speed of the work spindle is increased at J up to a high rate indicated at K while the tool is held in fixed rubbing finishing contact position with the work piece diameter B. This particular method of operation results in freedom from chatter and a high degree of finish for the work surface at the conclusion of movement of the cutting tool to depth.

After a. predetermined interval of time has elapsed. with the tools thus in dwell contact and with high speed spindle rotation taking .place, the work is stopped in rotation and then the cutting tool is retracted back to initial starting position B at a rapid traverse rate. The purpose of stopping the work rotation completely from withdrawing the tool from dwell position to retracted position is so that the cutting edge of the tool does not scrape against the finished face F of the crankshaft web A and gouge a spiral groove in this surface as it retracts backwardly to initial starting position. which would be the case if the work were rotating during this retraction movement.

As illustrative of a machine involving the above mode of operation and to which the hydraulic and electric operating and control mechanism of applicants invention is particularly well adapted, there is shown diagrammatically in Figure In a center drive linebearing crankshaft lathe having a frame I upon which is suitably mounted the center drive ring gear chuck II for gripping and supporting the crankshaft or work piece W and to rotate it at an appropriate cutting speed. The center drive ring gear chuck I is driven from the main drive motor I6 having a pulley I1 over which operates belts to drive the main drive pulley I5 which in turn is connected through suitable transmission gearing 22 to rotate the ring gear I.

Also mounted on the frame l of the machine is a pair of oppositely reciprocatable tool bars 05 and 1| each carrying appropriate cutting tools T. in this case adapted to be fed relative to the work axis I03 from opposite'sides thereof to perform cutting operations on the work piece. The ,tool bars 35 and 1| are actuated in oppositely reciprocatable motion by a pinion IOI carried on the rock shaft 83 which is suitably Journaled in the frame I of the machine. The pinion I III engages the respective racks 10 and 10a of the tool bars 35 and 1 I. Also fixed on the rock shaft 88 is the segmental gear BIwhich engages in the rack 33 connected to the piston rod or movable element 90 of the piston 88 of the main feed or fluid pressure actuating cylinder 81. Thus, reciprocation of the piston in the cylinder 81 by appropriately applying pressure thereto through the line I60 or I6I will afiect reciprocatory feeding and rapid traverse movement in the desired direction in the tool bars 65 and II and in the tools T mounted thereon. The feed movement of the tool bars is stopped at a predetermined fixed position by the engagement of the end 83a of the rack 83 with a fixed abutment stop screw I04 carried in the machine frame I.

On the rock shaft 88 is fixed a segmental or cam disc Ill. Disc II4 has a number of axially offset peripheral T-slots II1, whereby a series of cams I08a, IIOa,.IIIa, H6, and I52 are fixed in adjusted positions along the respective slots by means of T-head bolts II8. A bracket I01 is fixed to frame 8 adjacent the periphery of disc I I4, as by screws I08, and switching means comprising a series of switches I09, IIO, III, and I12 are fixed to said bracket in positions so that their switch arms are moved to circuit-closing position by the respective cams, as disc H4 is rotated in timed relation with feeding movement of the cutting tools. In addition, a valve III is attached to bracket I01 and has a plunger I23 positioned to be operated at a. selected time during each work cycle, by cam IIB.

Referring to Figures VI, VII, and VIII, valve I I3 consists of a valve body I I3a having hydraulic connections, two of which are shown at I10 and I12. The particular valve mechanism may be of the rotarybalanced type rate varying valve or any other well-known type, and hence need not be shown in detail. Sufiice it to say that an operating shaft I22 whose rotation operates to vary the effective passageway for fiuid through the valve, extends into a chamber I26 formed by a bracket II8 attached to valve I I3 by screws I2I. A pinion I23 is fixed upon shaft I22 by a key I24 and a lock nut I25. Bracket H9 is formed with a bore I29 whose axis extends tangentially of gear I23, and a plunger I28, having a rack I21 formed thereon, is slidably fitted within said bore with the rack teeth in mesh with gear I23. A groove I30 is formed longitudinally in plunger I28 and the squared end I3I of a pin I32 carried by bracket II9, projects into this groove and acts to limit the movement of plunger I28 to reciprocation. Plunger I28 is counterbored, as at I33, to receive one end of a spring I39, the other end of which is located within a hollow plug I40 closing the other end of bore I28. This spring therefore acts to urge plunger I28 outwardly toward cam disc I. The outward end of plunger I28 is forked as at I35; Figure V111, and has aligned holes within which a stud I36 is held by a nut I31. Stud I38 has a central cylindrical portion I36a whose axis is eccentric to the axis of stud I38, and a cam roller I33 is mounted upon portion I36a. By loosening nut I31 and applying a wrench to a socket head in stud I36, the latter may be adjusted to slightly vary the effective length of plunger I28 and thus provide for adjustment in setting said plunger with respect to cam II6. Thus, as disc H4 is rotated in timed relation with the feeding movements of the tools, cam II6 engages roller I33 and'reciprocates plunger I26 inwardly against the action of spring I39, to rotate gear I23 and actuate the valve mechanism to reduce the ef! fective passageway therethrough. The purpose of this will be subsequently explained as well as the function of switches I09, IIO, III and H2 in cooperation with disc H4 and the cams thereon.

Figure 111 is a diagram of the hydraulic and electrical control system of our invention and, for clarity, disc I I4 has been shown as extendin throughout 360 of arc, with the several cams and the switches controlled thereby, spaced about its periphery.

In our preferred embodiment, however, a segment extending through approximately 215 of arc is used, as shown in Figures IV and -V. It will be clear that there is nothing critical about the angular extent of said segment but that said extent may be greater or smaller depending upon the radius of sector gear 91, while, for any given angular size, the length of the cams will be correspondingly varied in accordance with the desired time relations of the various functions performed by the machine.

Fluid under pressure, is supplied by a fluid pressure pump I44 of any desired type, driven by a motor I45. Pump I44 draws fluid from a reservoir I49, through filters I41 and line I48. Drainage from a relief valve in the pump I44, for maintaining pressure in the line I50, is exhausted through the line I5I which returns the fluid to the reservoir I49. A delivery line leads by way of line I50, pilot pressure valve I53, line I54, feed valve I55, line I56, valve I51, line I58, check valve I59, and line I60, to cylinder 81, previously described.

Feed valve I55 is of the balanced three-way spring centered type having booster connections at each end from high pressure line I65 and drainage connections to line I61. A pair of solenoids b and c are connected to the valve core and, in conjunction with the valve spring, operate to move said core into three different positions depending, respectively, upon whether both 1) and c are de-energized, b only is energized, or 0 only is energized. When both solenoids b and c are de-energized, valve I55 acts to connect high pressure supply line I54 to forward traverse line I56, and service line I63 to exhaust line I64. When solenoid b only is energized, high pressure line I54 is connected to line I68 and line I56 is connected to exhaust line I64; and when solenoid c only is energized, high pressure line I54 is connected directly to exhaust line I64.

Valve I51 is of the spring offset two-way solenoid operated type having a high pressure booster connection from line I65 and a drainage connection to line I61. A solenoid a is provided II8, previously described. From valve II3 a line I12 connects to line I60, which, it will-be remembered, extends from check valve I59 to the upper end of cylinder 81. A branch line I14, connects lines I12 and I68 through a, check valve I69 so that fluid may flow from I14 into I68, but not in the reverse direction. A draining line I1I extends from valve II3 to reservoir I49.

Solenoid a of valve I51, is connected by a line IIIb with a forward traverse to feed switch III. Solenoid b of valve I55 is connected by a line I092) to return traverse and main motor control switch I09. A time relay I13 is inserted in line I09b so that solenoid b is energized a few seconds after operation of switch I09. A branch line I090 extends from line i096 and is effective through any well-known relay control, to open the circuit of the main driving motor I6. Solenoid c is connected so as to be energized automatically by and upon energization of motor I45, as by any well-known relay-controlled circuit. The circuit including soleoid c has a relay therein whereby, upon energization of switch II2, said circuit is opened and the solenoid is deenergized. In other words, the connections are such that solenoid c is energized only when motor I45 is operating and switch H2 is not energized.

The main driving motor I6 is a two-speed machine and has a circuitv connected to switch IIO so that, when said switch is closed by contact of cam IIOa, the motor speed is changed from lower to higher.

In operation motor I45 is started and solenoid c is thereby energized to shift valve I55 to posi tion connecting high pressure line I54 to exhaust lme I64 whereby fluid delivered to line I54 simply returns to reservoir I49. A work piece is loaded into the lathe and the main drive motor I6 is started to thus rotate the work piece at the speed corresponding to the slower speed ,pf motor I6. At this time, the operating arm of switch H2 is resting on cam I52, as shown in Figure IV; and it will be noted that all other cams are out of contact with their respective arms. Closing of the circuit to the main drive motor, {energizes switch H2 and opens the circuit to solenoid c, as aforesaid. Valve I55 is thereby operated to connect high pressure line I54 to forward traverse line I56, and to connect line I6I to exhaust line I64. Fluid under pressure now flows from line I56, through valve I51, and lines I58,

I to cylinder 81. Piston 89 and rack 93 are thereby forced downwardly at their maximum rate to rotate gear sector 91 and disc II4. At this time, fluid is exhausted from the lower end of the cylinder 81 by way of line I6I, valve I62,

line I63, and valve I55 to exhaust line I64. The tools are thus rapidly traversed toward the rotating work piece.

Just prior to contact of the tools with the work as, for example, when they are about to begin cutting down the cheeks of a crankshaft, cam II6'engages roller I33 and operates to partially close valve II3. A short interval thereafter cam IIIa engages and closes its switch III to thereby energize solenoid (1. Valve I51 is thereby operated to out off the passage from line I56 to I58. Fluid in line I56 is now forced to pass into line I68, and, since it cannot pass through check valve I69, it enters line I10, throughvalve H3, and line I12 to line I60. Since it cannot escape through check valve I59, it passes to cylinder 81 at a much reduced rate because of the 7 ore, the tools are fed into the work at reduced peed.

The feeding speed of, the tools is still further 1:radually reduced whena high riser on cam II6 'perates to further progressively restrict the flow f fluid through valve I I3 as the tools begin cuting the line bearings B of the work piece. lhortly thereafter, and at substantially the same ime, cam I09a engages and operates its switch '09, cam IIOa engages and operates its switch H0, and rack 93 engages stop pin I04 to thereby stop further feeding of the tools. Operation of switch IIO acts to speed up the driving motor I6 and rotate the work at an increased rate, to thereby finish the bearing surfaces to a high degree of accuracy. Due to time relay I13, this high speed finishing cut continues for a few seconds. Relay I13 then acts to energize solenoid b and also to stop driving motor I6. During the aforesaid finishing of the bearing surfaces, full pressure acts on piston 89' to hold rack 93 firmly against stop pin I04.

Energization of solenoid b operates valve I55 to connect high pressure line I54 to line I63,.

' 81 to force piston 89 upwardly and effect rapid retraction movement of the tools. During this movement, fluid above piston 89 exhausts through lines I60, I12, I14, valve I69, lines I68 and I56 to valve I55, thence to exhaust line I64. Simultaneously with retraction of the tools cam disc I I4 is reversely rotated until, when cam I52 contacts switch I I2, solenoid c is again energized and valve I55 is shifted to by-pass the delivery .of pump I44 from line I54 to exhaust-line I64. The tools are thereby brought to rest whereupon the finished work piece is removed and an unfinished one loaded into the machine to repeat the cycle just described.

The electric control circuit particularly illustrated in Figure IX is adjusted by the operator by a suitable manually operated control panel located on the machine for easy accessability to the operator.

Conditioning switch I83 is closed to connect main lines I84 and I85. Switch I86 'isthen closed whereupon hydraulic motor I45 is energized by way of line I85, switch I86, line I81, motor I45, line I88, and main line I89. At the same time, energization of motor I45 operates to close normally open relay I45a. As cam I52 is at this time closing switch II2, solenoid c of valve I55 is energized by way of line I85, solenoid 0, line I9I, normally closed relay I6a, line I93. closed relay I45a, line I94, and switch II2 to line I89. As previously described, valve I55 is thereby conditioned so that delivery of pump I44 through line I54, discharges directly to exhaust line I64.

A work piece is now loaded into the machine and switch I95 is closed to thereby energize main driving motor I6 by way of line I85, starting switch I95, stop switch I96, relay coil I91, normally closed relay I13b, motor I6, normally closed relay I99a, and line 200 to main line I89. Energization of coil I91 establishes a holding circuit by way of line I85, relay contacts I91a and line 20I, as will be obvious from inspection of Figure IX. Energization of motor I6 operates to open normally closed relay I6a to thereby de-energize solenoid c, whereupon, valve I55 is biased under influence of its springs to connect high pressure delivery line I64 to traverse line I56. The tools are now rapidly traversed toward the rotating work piece and segmental disc 4 and its cams are rotated as has been previously described. As

and switch III to main line I89. As previously described, energization of solenoid a operates to close valve I51 and divert fluid flow to cylinder 81, by way of now partially closed valve II3. Thereby, the speed of the. tools is reduced to the proper feeding value as they contact the work piece and begin to cut.

Cutting now proceeds at a feeding speed directly controlled by valve I I3 and cam I I6 until, as the final diameter of the work piece is approached, cams I09a and IIOa engage and close their respective switches I09 and H0 at substantially the same time.

Closure of switch I09 operates to energize relay coil I13 by way of line I 85, line 203. reconditioning switch 204, coil I13, line 205 and switch I09 and line I 89. However, as I13 is a time relay, it does not immediately act to operate its blades.

Closure of switch I I0 operates to energize relay coil I99 by way of lines I85, 206, coil I99 and switch IIO, to open normally closed blades I99a and to close blades I99b whereby a portion of the field coils of motor I6 are cut out and the motor speed is increased at substantially the same time as rack 93 engages and is positively stopped by pin I04. This operates to put an extremely accurate and highly finished surface upon the line bearings B of the work piece.

Motor I6 continues to rotate at high speed for a few seconds or until energized relay coil I13 acts to operate its blades. As soon as relay I13 acts, normally closed blades I13b are opened to deenergize and stop motor I6; to establish a holding circuit by way of line 201, blades I130 and line 208; and to close blades I13a. Closure of blades I13a operates to energize valve solenoid b by way of line I85, solenoid b, normally closed relay 2| Ia, line 2I9, now closed blades I13a, and lines M0 and I89.

Energization of solenoid b, as previously described, operates to condition valve I so that high Pressure line I 54 is connected to retraction line I63 'while traverse line I68 is connected to exhaust line I64. Fluid is now forced through lines I63 and I6I to the retraction side of piston 89 to rapidly retract the tools and reversely rotate segmental disc II4. Rotation of dam IIIa out of contact with switch III and de-energize solenoid a, has no effect since fluid forced out by upward movement of piston 89 can flow only to line I68 and exhaust line I64. Because of its holding circuit, relay coil I13 remains energized when cam I09a rotates out of contact with its switch, and the circuit energizing solenoid b remains closed while the circuit of motor I6 remains open with consequent closure of blades I Be.

As soon as cam I52 again contacts and closes switch II2, solenoid c is energized and relay coil .2 again opens the normally closed blades 2| Ia,

deenergizes solenoid b and conditions valve I55 to connect delivery line I54 directly to exhaust. Since solenoid b is not required to operate at the direction reversely shifts the armature of solenoid b.

' As delivery of pump I is now diverted directly to exhaust, retraction movements of the tools cease and all parts of the lathe come to rest. Stop or reconditioning switch I96 is now manually operated and as this switch is mechanically connected with the blades of switch 204, as

indicated by the dotted line 2l2, Figure IX, the circuit through time relay coil H3 is broken, blades I131) close, "3a open, andthe holding circuit 201, 208 is broken.

The lathe is now in condition for a new cycle of operations. The finished work piece is removed, the lathe reloaded, and switch I95 is closed to initiate a cutting cycle. When the machine is to remain idle for any appreciable period of time, switch I83 is manually operated to open all circuits that might be closed, such as the one servicing motor I".

From the foregoing description, it will be clear that we have provided a lathe that is well adapted for automatic and rapid finishing of articles such as crankshafts. All cuts are made in one pass of the cutting tools, and all tools operate simultaneously upon the article being turned. Our lathe is rapid in operation for not only are all cuts made in one pass of the tools, but traverse and retraction movements are efiected at high speed while the tools are slowed to proper feeding speed just before cutting begins. .During the initial cuts, such as in facing the cheeks of a crankshaft, where the highest accuracy is not required, the feeding of the tools may proceed at a relatively rapid rate, while, because of the action of valves I51 and H3, in cooperation with cam I IS, the feeding speed may be reduced to any desired value. In fact, by providing a cam I I6 having the desired contour, the feeding speed may be varied in any desired sequence. It is within the purview of our invention to provide cams H6 that are given the proper contour to effect correct feeding speeds for each individual job or type of work piece. At-the moment that the tools have substantially completed the line bearing surfaces, their feeding movement is positively stopped, the driving motor is automatically speeded up and a high precision finish is given to the bearing surfaces during the few seconds that such rapid way valve having a flrst and a'second actuating solenoid for shifting said valve each side of an intermediate position, fluid conduit means for connecting said pump to said valve, a two-way,

valve having a third actuating solenoid, fluid conduit means connecting said three-way valve to said two-way valve, fluid conduit means connected between the output from said two-way valve to the forward pressure chamber of said actuating cylinder including a check valve limiting flow from said two-way valve to said cylinder, fluid conduit means connected between said three-way valve and the return pressure chamber of said actuating cylinder, a rate varying valve having its input connected to the fluid conduit means between said three-way and said two-way valves, fluid conduit means connecting the output from said rate varying valve to the forward pressure chamber of said actuating cylinder, a check valve connected across the input and output of said rate varying valve to allow free flow from the forward pressure chamber of said fluid pressure actuating cylinder to the fluid conduit means between the three-way and two-way valves, and an electrical circuit connected to said solenoids, including switching means actuated by the movement of the movable element of said fluid pressure actuating cylinder.

2. In a control circuit for a fluid pressure actuating-cylinder, a fluid pressure pump, a three-way valve having a first and a second actuating solenoid for shifting said valve each side of an intermediate position, fluid conduit means for connecting said pump to said valve, a two-way valve having a third actuating solenoid, fluid conduit means connecting said three-way valve to said two-way valve, fluid conduit means connected between the output from said two-way valve to the forward pressure chamber of said actuating cylinder including a check valve limiting flow from said two-way valve to said cylinder, fluid conduit means connected between said three-way valve and the return pressure chamber of said actuating cylinder, a rate varying valve having its input connected to the fluid conduit means between said three-way and said two-way valves,

rotation takes place until relay I13 acts to stop the driving motor and effect rapid retraction of the tools.

While, for the purpose of complying with the patent statutes, we have selected-and described a machine adapted for a particular job, it willbe understood that the invention is not so limited, but that numerous other types of work may be turned 4. the lathe and correctly handled by various contours and adjustments of the cams. Furthermore, numerous modifications and substitutions will occur to those skilled in this art. It is our intention to reserve all such modifications and substitutions as fall within the scope of the subioined claims. I

Having thus fully set forth and described this invention, what is claimed as new and desired to be secured by United States Letters Patent is:

1. In a control circuit for a fluid pressure actuating cylinder, a fluid pressure pump, a threefluid conduit means connecting the output from said rate varying valve to the forward pressure chamber of said actuating cylinder, a check valve connected across the input and output of said rate varying valve to allow free flow from the forward pressure chamber of said fluid pressure actuating cylinder to the fluid conduit means between the three-way and two-way valves, and an electrical circuit connected to said solenoids, including switching means actuated by the movement of the movable element of said fluid pressure actuating cylinder, said switching means including a first switch connected to said flrst solenoid'actuable to energize said solenoid to shift said three-way valve to connect fluid pressure from said pump to said two-way valve, a second switch connected to the third solenoid of said two-way valve actuable to energize said solenoid to close off said valve to prevent fluid flow into the conduit connected to the forward pressure tuating cylinder, a fluid pressure pump, a threeway valve having a first and a second actuating solenoid. for shifting said valve each side of an valve having a third actuating solenoid, fluid conduit means connecting said three-way valve to said two-way valve, fluid conduit means connected between the output from said two-way valve to the forward pressure chamber of said actuating cylinder including a, check valve limiting flow from said two-way valve to said cylinder, fluid conduit means connected between said threeway valve and the return pressure chamber of said actuating cylinder, a rate varying valve hav ing its input connected to the fluid conduit means between said three-way and said two-way valves, fluid conduit means connecting the output from said rate varying valve to the forward pressure chamber of said actuating cylinder, a check valve connected across the input and output of said rate varying valve to allow free flow from the forward pressure chamber of said fluid pressure actuating cylinder to the fluid conduit means between the three-way and two-way valves, and an electrical circuit connected to said solenoids, including switching means actuated by the movement of the movable element of said fluid pressure actuating cylinder, said switching means including a first switch connected to said first solenoid actuable to energize said solenoid to shift said three-way valve to connect fluid pressure from said pump to said two-way valve, a second switch connected to the third solenoid of said two-way valve actuable to energize said solenoid to close off said valve to prevent fluid flow into the conduit connected to the forward pressure chamber of said cylinder, and an electric delay timer switch connected to said second solenoid of said three-way valve to energize said solenoid after a predetermined interval has elapsed from the time it is initially actuated, and abutment means engaged by the movable element of said fluid pressure actuating cylinder to positively arrest the forward movement of said element in a predetermined position.

4. In a control circuit for a fluid pressure actuating cylinder, a fluid pressure pump, a threeway valve having a first and a second actuatin solenoid for shifting said valve each side of an intermediate position, fluid conduit means including a pilot pressure valve for connecting said pumpvto said valve, a two-way valve having a third actuating solenoid, fluid conduit means connecting said three-way valve to said two-way valve, fluid conduit means connected between the output from said two-way valve to the forward pressure chamber of said actuating cylinder including a'check valve limiting flow from said twoway valve to said cylinder, fluid conduit means connected between said three-way valve and the return pressure chamber of said actuating cylinder, a rate varying valve having its input connected to the fluid conduit means between said three-way and said two-way valves, fluid conduit means connecting the output from said rate varyin valve to the forward pressure chamber of said actuating cylinder, a check valve connected across the input and output of said rate varying valve to allow 'free flow from the forward pressure chamber of said fluid pressure actuating cylinder to the fluid conduit means between the three-way and two-way valves, and an electrical circuit connected to said solenoids including switching means actuated by the movement of the movable element of said fluid pressure actuating cylinder.

5. In a control circuit for a fluid pressure actuating cylinder, a fluid pressure pump, a threeway valve having a first and a second actuating solenoid for shifting said valve each side of an intermediate position, fluid conduit means for connecting said pump to said valve, a two-way" valve having a third actuating solenoid, fluid conduit'means connecting said three-way valve to said two-way valve, fluid conduit means connected between the output from said two-way valve to the forward pressure chamber of said actuating cylinder including a check valve limiting flow from said two-way valve to said cylinder, fluid conduit means including a back pressure valve connected between said three-way valve and the return pressure chamber of said actuating cylinder, a rate varying valve having its input connected to the fluid conduit means between said three-way and said two-way valves, fluid conduit means connecting the output from said rate varying valveto the forward pressure chamber of said actuating cylinder, a check valve connected across the input and output of said rate varying valve to allow free flow from the forward pressure chamber of said fluid pressure actuating cylinder to the fluid conduit means between the three-way and two-way valves, and an electrical circuit connected to said solenoids, including switching means actuated by the movement of the movable element of said fluid pressure actuating cylinder.

6. In a control circuit for a fluid pressure actuating cylinder, a fluid pressure pump, a threeway valve having a first and a second actuating solenoid for shifting said valve each side of an intermediate position, fluid conduit means including a pilot pressure valve for connecting said pump to said valve, a two-way valve having a third actuating solenoid, fluid conduit means connectingsaid three-way valve to said two-way valve, fluid conduit means connected between the output from said two-way valve to the forward pressure chamber of said actuating cylinder including a check valve limiting flow from said twoway valve to said cylinder, fluid conduit means including a back pressure valve connected between said three-way valve andthe return pressure chamber of said actuating cylinder, a rate varying valve having its input connected to the fluid conduit means between-said three-way and said two-way valves, fluid conduit means connecting the output from said rate varying valve to the forward pressure chamber of said actuating cylinder, a check valve connected across the input and output of said rate varying valve to allow free flow from the forward pressure chamber of said fluid pressure actuating cylinder to the fluid conduit means between the three-way and twoway valves, and an electrical circuit connected to said solenoids, including switching means actuated by the movement of the movable element of said fluid pressure actuating cylinder.

The following references are of record in the file of this patent:

UNITED STATES PATENTS Date Number Name 2,138,964 Groene Dec. 6, 1938- 2,191,935

Groene Feb. 2'7, 1940 

